Casing machine

ABSTRACT

Upright containers are fed into the casing machine from a multiple lane supply line, assembled into one tier, and the tier is transferred and reoriented by tiering fingers which deposit the containers in a tiering chamber. The open end of an empty case is manually positioned adjacent the tiering chamber, and pusher feet insert the tier in the case. A feature of the casing machine is a rocking differential which smoothly accelerates and decelerates the tiering fingers to prevent damage to the containers. Other features include a timing pin and chain mechanism which can be manually adjusted to control the number of tiers loaded into a case, rapid change structure in the zone where the tiers are assembled so that the machine is readily adaptable to handle a range of container sizes, and a lowerator mechanism under positive mechanical control for gently lowering the loaded cases to a discharge position.

Unite States atent [m 111 3,729,85

Schlueter et al. Apr. 24, 1973 CASING MACHINE [75] lnventorszDavid F.Schlueter, Hoop eston. Primary Emminr Edward A'Sroka Vermilion UL; MyronC. Noble Att0rneyFrancis W. Anderson St. Joseph, Ind.

I v [57] ABSTRACT [73] Assigneei FMC Corporation San Jose, Calif Uprightcontainers are fed into the casing machine [22] Filed Oct 19 1970 from amultiple lane supply line, assembled into one tier, and the tier istransferred and reoriented by tier- [21] Appl. No.: 82,044 ing fingerswhich deposit the containers in a tiering I chamber. The open end of anempty case is manually Relaed Apphcanon Data positioned adjacent thetiering chamber, and pusher [62] Division of Ser. No. 757,876, Sept. 6,1968, abanfeet insert the tier in the case. A feature of the casingdoned. machine is a rocking differential which smoothly accelerates anddecelerates the tiering fingers to prevent [52] US. Cl. ..l98/25, 198/33AD damage to the containers. Other features include a [51] Int. Cl..B65g 47/24 timing pin and chain mechanism which can be [58] Field ofSearch; ..l98/25,33 AD, 209, manually adjusted to control the number oftiers 198/211; 9 loaded into a case, rapid change structure in the zonewhere the tiers are assembled so that the machine is 1 References Citedreadily adaptable to handle a range of container sizes, 1 and alowerator mechanism under positive mechanical UNITED STATES PATENTScontrol for gently lowering the loaded cases to a 2 545 325 7 1953discharge position. 1,461,222 7/1923 4 Claims, 33 Drawing FiguresPatented April 24, 1973 15 Sheets-Sheet 2 N 0Q uww mmu 5N mm PmINVENTQRS DAVID F SOHLUETER MYRON C. NOBLE M mi-Hi ATTORNEYS PatentedApril 24, 1973 15 Sheets-Sheet 4 INVENTORS DAVID E SCHLUETER MYRON G.NOBLE BY 1w. W

2 O mmkEIm 240 km: mmImDm m e. a Fa 2 0 mxOmkm mmImDm ATTORNEYS PatentedApril 24, 1973 3,729,085

15 Sheets-Sheet 5 94. INVENTORS 96 \Q2 DAVID F. SOHLUETER 98 mmou c.NOBLE BY Jw MW mew;

ATTORNEYS Patented April 24, 1973 15 Sheets-Sheet 6 INVENTORS DAVID F.SCHLUETER MYRON O. NOBLE ATTORNEYS Patented April 24, 1973 3,729,085

15 Sheets-Sheet 7 INVENTOR. DAVID F. SCHLUETER MYRON c. NOBLE' ATTORNEYSPatented April 24, 1973 3,729,0s5

l5-Sheets-Sheet 8 RPM DIFFERENTIAL loo OUTPUT GEAR |42 3 DIFFERENTIALINPUT GEAR |4| so 'oNE REVOLUTION OF 20 INPUT GEAR |4| AND DIFFERENTIALCAM-65 O I I i 0 9'o I 150 2"ro 3e'o SHIFTER SHIFTER STROKE RETURN STARTRETURN LOWER RETRACT CONTAINERS Q IN CASE PUSH E I [ii l 2 INVENTORSDAVID F. SOHLUETER MYRON G. NOBLE ATTORNEYS Patented April 24, 19733,729,085

15 Sheets-Sheet 1) INVENTORS DAVID F. SGML ER MYRON C. NOBL ATTORNEYSPatented April 24, 1973 15 Sheets-Sheet ll INVENTORS D D F. SOHLUETER MON 6. NOBLE ATTORNEYS Patented April 24, 1973 15 Sheets-Sheet 12PHOTOELECTRIC UNIT INVENTORS DAVID F. SGHLUETER MYRON c. NOBLE ATTORNEYSPatented April 24, 1973 15 Sheets-Sheet 15 1Q @LAQL Q INVENTORS DAVID F.SCHLUETER MYRON G NOBLE J Lu ATTORNEYS Patented April 24, 1973 15Sheets-Sheet l4 INVENTORS DAVID F. SCHLUETER 3 MYRON C.NOBLE TTORNEYSPatented April 24, 1973 15 Sheets-Sheet 15 INVENTORS 1 DAVID E SGHLUUERmnou c. NOBLE ATTORNEYS CASING MACHINE This is a division of applicationSer..No. 757,876 filed Sept. 6, 1968, now abandoned.

BACKGROUND OF THE INVENTION 1. Field ofthe Invention The presentinvention relates to container handling machines, and particularly tomachines which insert a tier or tiers of containers into a case. Morespecifically, the invention concerns casing machines of the typeincluding sets of aligned tiering fingers which lift multiple .row tiersof upright containers froma centrally apertured separator adjoiningthe'end of a container supply line, and which reorientandtransfer thetier of containers to a tiering chamberfrom which they are insertedendwise into a case.

2. Description of the Prior Art The present invention concerns a casingmachine of the type disclosed in U.S. Pat. No. 2,650,009 to Kerr, andassigned to the assignee of the present invention.

.One disadvantage of the Kerr apparatus is that untainers are subjectedto shock and/or denting because the tiering fingers are moving nearmaximum velocity at the time they engage the containers. Additionalshock and jarring is experienced by the containers as they aretransferred onto the floor of a tiering chamber because the tieringfingers which effect'the transfer, travel at a constant velocity. Also,containers whose height is approximately equal to or less than theirdiameter tend to become disoriented when entering the tiering chamber ata high velocity and the top rows of containers tend to tip forwardly.

Pusher feet in the patented structure transfer the tiers of containersinto a case. The pusher feet trace a path similar to a parallelogram ina vertical plane, and the forward and rearward cycles are identical. Theresulting motion is quite rapid, tending to upset tiers of short cans,and the case flaps are sometimes torn by the pusher feet due to theirimmediatelifting in the rearward stroke.

SUMMARY OF THE INVENTION BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is aperspective of the casing machine of the present invention, with theinlet end of the machine at the right.

FIG. 2 is a perspective of the casing machine viewed from the sideopposite to the side shown in FIG. 1.

FIG. 3 is a perspective of the casing machine viewed from its inlet end.

.FIG. 4 is a perspective of the drive train of the casing machine.

FIG. 5 is an enlarged, fragmentary elevation of a shifter mechanismwhich controls the flow of containers into the casing machine and isviewed in a downstream direction.

FIG. 6 is a section taken on lines 6--6 of FIG. 5.

FIG. 7 is a fragmentary perspective of two divider units whichcooperatively define a lane for a row of cans in the area indicated bythe arrow 7 on FIG. 1.

FIG. 8 is an enlarged section taken along lines 8--8 on FIG. 7.

FIG. 9 is a perspective of a rocking differential indicated by the arrow9 on FIG. 4.

FIG. 9A is a section, at reduced scale, taken through the center of therocking differential shown in FIG. 9.

FIG. 10 is a diagram showing the input and output speeds of the rockingdifferential.

FIG. 10A is an elevation of a cam and follower arm, shown in the FIG. 4drive train, for rocking the differential.

FIG. 11 is a perspective of pushers, and their mounting and actuatingmembers, viewed from below, that push atier of containers into a case.

FIG. 11A is a fragmentary plan indicated by the arrow 11A on FIG. 11.

FIG. 12 is a trace of the motion of the pushers shown in FIG. 11.

FIGS. 13-16 are fragmentary elevations of a synchronization controlshown in FIG. 2, and illustrate successive operational positions of thecontrol elements.

FIGS. 17 and 17A are enlarged fragmentary plans of an inactive and anactive timing pin, respectively, which are part of the synchronizationcontrol.

FIG. 18 is a perspective primarily illustrating a lowerator whichsupports an empty case in filling position, and lowers the filled caseto a discharge position.

FIG. 18A is an elevation of a lowerator cam which actuates the loweratorshown in FIG. 18.

FIG. 18B is a fragmentary elevation of a trip lever mechanism partiallyshown in FIG. 18.

FIG. I9 is a schematic electrical control diagram.

FIGS. 20 and 20A are fragmentary, diagrammatic elevation and plan views,respectively, which illustrate the inlet end portion of the casingmachine and an associated supply conveyor.

FIGS. 21 and 21A are diagrammatic elevation and plan views,respectively, illustrating a mechanism for sensing when each of aplurality of longitudinal rows of can in one assembled tier is complete.

FIGS. 22-26 are fragmentary diagrammatic elevations illustrating theoperational sequence of assembling tiers of cans and loading the tiersin a case.

DESCRIPTION OF THE PREFERRED EMBODIMENT General With reference to FIGS.1 and 2126, upright containers, such as cans C, are supplied to thecasing machine 20 by a multi-lane feed conveyor 22 which is driven fromthe casing machine. The cans are divided into multiple lanes on theconveyor by conventional means not shown and are separated by lanedividers 24 (FIG. 1). The cans pass through a transversely movableshifter 26 whose vertical partitions 27 are initially aligned with thelane dividers 24.

The cans advance into a separator 28 having vertical partitions 29 inalignment with the lane dividers 24. When all lanes in the separator 28are completely filled to constitute one tier of a case, a can stop andsensing mechanism 30 in each lane is actuated to initiate a can transferor tiering cycle.

Certain drive mechanism of the casing machine is now actuated, causingthree sets of equally spaced tiering fingers 32 to rotate 120 degreesabout a common support shaft. This moves shifter mechanism 26 laterallyto temporarily interrupt the flow of incoming cans. The tier up uprightcans are lifted from the separator 28 by one set of tiering fingerswhich reorients the tier 90 and deposits the tier on edge, with the cansin a lying down position, in a tiering chamber 34.

After the desired number of tiers of cans has been assembled in thetiering chamber 34, pusher feet 36 are actuated to move the tiers into acase A which has been manually positioned over a nozzle 38 and issupported by a lowerator 40. The filled case is then lowered to adischarge conveyor or the like by the lowerator.

After the removal of the filled case, placement of an empty case on thenozzle 38 swings the lowerator 40 to its raised position supporting theempty case.

Power Train With more specific reference to the casing machine 20, poweris supplied from a motor M (FIGS. 3 and 4) through a speed reducer R toa power shaft 42. Shaft 42 rotates continuously and supplied powerthrough a sprocket and chain drive 44 to the feed conveyor 22.

A tiering input shaft 46 and a pusher-lowerator shaft 48 arerespectively driven by single revolution clutches 50 and 52. On theirdriving sides, the clutches have sprockets 54 and 56 (FIG. 4) which areconnected by a chain 57 to a sprocket 58 mounted on the power shaft 42.Shafts 46 and 48 are driven only when their respective clutches 50 and52 are engaged, but the sprockets 54 and 56 rotate continuously in thedirections indicated by the arrows in FIG. 4.

When the single revolution tiering clutch 50 is engaged, the tieringinput shaft 46 rotates in the same direction as the sprocket 54. Theshaft 46 rotates a shifter cam 60 and a differential cam 61 that drivesone side of a rocking differential 62. The differential 62 whichoperates the tiering fingers 32. The output of the differential 62drives a sprocket 63 freely mounted on shaft 46. Sprocket 63, by meansof a chain 67, drives a tiering sprocket 64 which is attached to one oftwo spaced spiders 65 that are mounted on a tiering shaft 66.

One set of tiering fingers 32 is mounted on each of three cross-shafts63 which are carried by the spiders 65. A three to one speed reductionfrom the differential output sprocket 63 to the tiering sprocket 64causes the tiering fingers 32 to be rotated 120 degrees for eachcomplete revolution of the tiering input shaft 46.

Upon engagement of the clutch 52, (FIG. 4) a constant rotation isimparted to the pusher-lowerator shaft 48. The vertical motion of thepusher feet 36 is con trolled by a pusher lift cam which is mounted onthe shaft 48 and actuates a pusher lift arm 72 by means ofa pivotedpusher lift lever 73 having a follower roller engaged with the cam. Thehorizontal motion of the pusher feet 36 is effected by a pusher strokecam 74 which is mounted on the shaft 48 and actuates a pusher strokefollower arm 75.

As the result of mounting both the pusher lift and stroke cams on acommon shaft 48, their resultant motions are coordinated with alowerator cam 76 on the same shaft 48. The lowerator cam motion istransmitted to the lowerator 40 by a rod 77 (FIGS. 4 and 18A) which isactuated by a cam follower arm 79.

VARIABLE STROKE SHIFTER The variable stroke shifter 26 (FIGS. 1 and 5)functions as a blocking device to interrupt the flow of containers fromthe feed conveyor 22. For this purpose, a shifter bar 78 is displacedone-half ofa can diameter so that each of a plurality of the verticalpartitions 27 is placed in blocking relation to an incoming row of cansbetween the lane dividers 24 of the feed conveyor 22.

The shifter bar 78 (FIGS. 5 and 7) carries a depend- I ing shifterbracket 88, and slides on a spacer plate 80. Each end of the spacerplate 80 is supported by and secured to a block 81, as shown in FIG. 5.Downwardly open recesses 83 in the spacer plate 80 locate and retain aplurality of support arms 82, one of which is provided for each of theseparator plate partitions 29.

The shifter bracket 88 has side ribs 89 (FIG. 6) that slide in groovedguide bars 90. The guide bars 90 are mounted on a pair of transverse tiebars 84 that interconnect longitudinal side frame members 86. Theshifter bracket 88 (FIG. 5) includes a depending arm 91 having a seriesof holes 92 which provide for adjustment of the amount of lateralshifter stroke for various diameter cans.

Thus, a follower roller 94 is mounted in a selected hole 92corresponding to the desired shifter bar displacement, and so mounted,rides in a slot 96 in a shifter cam follower lever 98. The lever 98 ispivotally mounted to the frame of the machine at 99 and is oscillatedbetween the phantom and full line positions shown by a cam follower 100which is engaged withthe shifter cam 60.

Separator After passing between the partitions 27 through the shifter 26(FIG. 1) the cans C enter the lanes defined by the partitions 29 (FIG.7) of the separator 28. Opposite site sides of the cans are supported byramps 101, adjacent pairs of which are spaced apart so that the tieringfingers 32 can pass upward between the ramps to lift the containers. Theseparator 28 includes multiple divider units 102. Each divider unit isprovided with a pair of the ramps 101, one of the partitions 29, and isremovably mounted on the tie bars 84 by means of a bolt 104 recessed inthe support arm 82. The tie bars 84 cooperatively form a T-shaped slot105, and a square nut 106 which fastens the bolt 104 is captured in theslot 105.

The divider units 102 are positioned to accept a particular diameter ofcan between adjacent partitions 29 by first removing the spacer plate80, and then loosening the bolts 104 and sliding the support arms 82along the tie bars 84. Thus, by substituting a different spacer plate80, the interspacing of the partitions 29 can be changed to accept adifferent can size. If a different number of lanes are required, as wellas different lane sizes, the divider units 102 are readily removed bysliding the loosened unit along the slot 105 to a cross-slot 108 (FIG.7). The divider unit is then removed by sliding it forwardly out of thecross-slot. Other units can be added in the obvious, reverse procedure.This mechanism forms the subject matter of our aforesaid parentapplication.

Can Stop and Sensing Mechanism With continued reference to FIG. 7, oneof the can stop and sensing mechanism 30 is mounted on each divider unit102. Its purposes are to control the number of cans allowed toaccumulate in each lane of the separator 28, to control the longitudinalposition of the row of cans so that the cans do not partially extendinto the shifter 26, and to actuate a control circuit when this lane andthe other lanes are full of cans. This mechanism also forms the subjectmatter of our aforesaid parent application.

The can stop and sensing mechanism 30 for each lane is actuated by theleading can in the row of cans pressing against an upstanding stopfinger 110 which is mounted for limited displacement in a downstreamdirection. When so displaced, the mechanism 30 actuates a flag 112 thatinterrupts a light beam LB projected across the casing machine. When alllanes of the separator 28 are completely filled and all of the flags 112have been actuated to clear the light beam, a later describedphotoelectric control unit is energized to initiate a loading of theassembled containers into the tiering chamber 34 (FIG. 1).

Referring to FIGS. 7 and 8, the can stop fingers 110 is rigidly mountedon a support block 116. The support block 116 is adjustable axially of athreaded rod 118 which is engaged with a threaded aperture in the block,and slides on a' guide rod 120. The ends of the threaded rod 118 arerotatably mounted in spaced carriage blocks 124 and 126, and the guiderod 120 is rigidly secured in the carriage blocksBy turning a nut 130fixed on one end of the threaded rod 118, the support block 116 and thecan stop finger 110 mounted thereon are moved along the guide rod 120 tolongitudinally adjust the can stop finger 110 for the desired row-lengthof cans to be accumulated in the corresponding lane. It is believedapparent that because the partitions 29 of two adjacent divider units102 form the lateral limits of one lane of cans, the outermost dividerunit at the left side of the casing machine (viewed in a downstreamdirection) does not require a can stop finger 110 or a flag 112.

Each carriage block 124 and 126 depends from the support arm 82 in themanner shown for the carriage block 126 in FIG. 8. Thus, each carriageblock is provided with a central upstanding tab portion 125 that extendsupward into a downwardly open milled slot 127. The tab is provided witha diagonal slot 133 and is retained by a roller 134, mounted on a pin135, which is disposed in the slot. With this construction, the assemblyincluding the carriage blocks 124 and 126, can stop finger 110, and thesupport block 116 gravitate to the upstream position illustrated, butmove downstream and diagonally upward when a lane of cans pushes againstthe can stop 110. These movements control the flag 112 to mask or unmaskthe light beam LB.

The flag 112 is pivoted to the support arm 82 by the pivot pin 135, andis pivoted to the carriage block 126 by a pivot stud 136. Accordingly,when the lane of cans pushes against the can stop finger 110, the pivotstud 136 is moved away from the pivot pin and the flag 112 swings aboutthe pin 135 out of the light beam LB, as indicated by the arrow 1 12a.

The light beam LB originates from a photoelectric unit 137 (FIG. 3)which includes an integral lamp and receiving element and is mounted onone of the frame members 86. The projected light beam LB is received bya reflector 139 which returns the beam to the receiving element of thephotoelectric unit 137. Since the light beam is interrupted by any oneof the flags 112 in rest position, thus indicating that one or morelanes of cans is not yet complete, the photoelectric unit generates acontrol signal only when the separator 28 accumulates a complete tier ofcans. The signal from the photoelectric unit 137 energizes an adjacentsolenoid 140 which in turn causes clutch 50 (FIG. 4) to engage andinitiate the tiering cycle.

Rocking Differential As previously indicated, and in accordance with thepresent invention, the set of tiering fingers underlying the cans in theseparator are smoothly accelerated upward to pick up cans from theseparator and are smoothly decelerated as the cans are deposited in thetiering chamber by the tiering fingers. In the illustrated embodiment ofthe invention this smooth acceleration and deceleration is performed bythe rocking differential 62 (FIGS. 4, 9 and 9A).

The rocking differential 62 provides a variable speed drive connectionfrom the tiering input shaft 46 to the tiering shaft 66, via rotation ofa pair of bevel gears 14] and 142 which are meshed with a spider gear144. When the solenoid 140 (FIG. 3) actuates the tiering clutch 50 (FIG.4) to transfer one tier of cans from the separator 28 (FIG. 1) to thetiering chamber 34, the tiering shaft 66 is turned 120 by the rockingdifferential 62 and the drive train including sprockets 63 and 64, andthe chain 67. During each tier transfer cycle, the spider gear 144 (FIG.9) of the rocking differential is first translated about the axis of theshaft 46 in the direction of the arrow 144a to subtract motion from thedrive chain 67 while the tiering fingers 36 lift the cans from theseparator 28. While the lifting movement continues, the spider gear 144is then moved bodily in the opposite direction, indicated by the arrow144b, to add motion to the drive chain 67 and accelerate the tieringfingers. During the tiering cycle, the rate of motion of the spider gearin the direction of the arrow 14412 is reduced to decelerate the tieringfingers and then reversed to bring the fingers to a smooth stop.

Referring to FIGS. 9 and 9A, both the gear 141 at the input side of thedifferential and the differential cam 61 are keyed to the tiering inputshaft 46. The gear 142 at the output side is pinned to the sprocket 63.The gear 142 and the sprocket 63 rotate together freely on the shaft 46,so that their motion can be modified by fore and aft motion of thespider gear 144.

The spider gear 144 rotates on a stub shaft 146 that projects from aspider gear hub 148, and the hub rotates freely on the shaft 46. Thus,oscillation of the spider gear hub 148 will add to and subtract from thedrive motion transmitted from the shaft 46, by means of the gears 141,144 and 142, in accordance with known principles ofdifferential gearing.

The oscillation of the spider gear hub 148 is provided by thedifferential cam 61 and associated linkage, as will now be described.The cam has a track 151 which is eccentric to the shaft 46. A camfollower 152 rides in the cam track and hence oscillates a cam followerlever 154 which is pivoted to the frame of the machine by a pivot shaft156.

The lower end of the cam lever 154 is pivoted at 157 to one end of a camlink 158. The other end of the cam link is pivoted at 159 to a cam crank160. The crank 160 depends from one end of a sleeve 162 that turnsfreely on the power shaft 42.

Depending from the other end of the sleeve 162 is a companion crank 163which is pivoted at 164 to one end of a spider link 165. The other endof the spider link is pivoted at 166 to a spider crank 167 that dependsfrom the spider gear hub 148.

Rotation of the tiering shaft 46 one revolution, by actuation of thetiering clutch 50 (FIG. 4) turns the differential cam 61 one revolution,the eccentric thus driving the cam lever 154 between its two limits ofswinging movement. This movement of the cam lever oscillates the spidergear hub 148 and the spider gear 144 fore and aft via the cam link 158,cam crank 160, sleeve 162, companion crank 163, spider link 165 andspider crank 167.

The oscillation of the spider gear 144 is superimposed on the motiontransmitted by the spider gear 144 to the chain 67 so that the tieringshaft 66 (FIG. 4) rotates with non-uniform motion to accelerate anddecelerate the tiering fingers 32 in the manner previously described.

FIG. 10 is a diagram showing the speed change in revolutions per minuteof the differential output gear 142, and hence the rotation of the shaft66 which carries the tiering fingers 32, during one rotation of thedifferential input gear 141. FIG. 10A illustrates the relation of thedifferential cam 61 to the FIG. 10 diagram; the degree markings on thecam are the same degree markings of the base line of the FIG. 10diagram. Reference should also be made to the later described FIG. 22which illustrates the can transfer operation of the tiering fingers 32.The abscissa of FIG. 10 is marked in 90 increments for one completerevolution of the input gear 141 and the differential cam 61. The speedof the input gear 141 is seen to be 60 RPM from the scale along the leftmargin of the dia gram. Starting at the differential cam 61 rotates at60 RPM upon energization of the tiering clutch 50 to drive the shaft 46.From the 0 reference point (FIG. A) the cam follower 152 moves towardthe shaft 46,

whereby the spider gear hub 148 (FIG. 9) is driven rearward in thedirection of the arrow 144a. This subtracts from the linear speed of thechain 67 which powers the tiering fingers so that the tiering fingersstart slowly from their rest positions. It will be seen that the 090quadrant of the cam track 151 will decelerate the movement of thedifferential hub 148 in the direction of the arrow 144a. Accordingly,the output gear 142 gradually accelerates from 0 to 90.

The lowest point of the cam track 151 is at 90 degrees, and the camfollower 152 is at its extreme of movement inwardly toward the shaft 46.Accordingly, at 90 degrees the spider hub 148 is briefly motionless andthe differential 62 transmits the full 60 RPM rotation of the inputshaft 46 to the output gear 142. Translated into movement of the tieringfingers 32 (FIG. 1), this means that the tiering fingers underlying thecharge of cans in the separator 28 rapidly accelerate after contactingthe cans at the beginning portion of the can transfer movement.

Between 90 and 180, the cam follower 152 moves outward from the shaft 46and drives the spider hub 148 (FIG. 9) forward in the direction of thearrow 144b. This adds to the linear speed of the chain 67 which powersthe tiering fingers. It will be noted that the 90l portion of the camtrack 151 is symmetrical with the 090 portion. Consequently, the l 80rotation of the output gear 142 smoothly acclerates the tiering fingersfrom 60 RPM to their maximum speed of RPM as the cam 61 rotates to itsposition. It should be noted that the hub 148 at this time has notattained its forward limit of movement in the direction of the arrow14411.

From 180 to 270, the cam follower 152 continues to move outward, and thehub 148 forward, although at a reduced rate. Therefore, the speed of theoutput gear 142 is reduced from its maximum at 180 of cam rotation dueto the reduced rate of forward rotation of spider hub 148. At 270 thecam follower 152 has reached its maximum outward excursion and thespider hub 148 is again stationary, as at 90, transmitting the 60 RPMinput gear rotation to the output gear 142.

As the cam follower moves from 270 back to 0, the spider hub 148 ismoved rearward in the direction of the arrow 144a and reduces the speedof the output gear 142 from 60 RPM to 0 RPM. The tiering fingers duringthis latter movement thus decelerate the can charge as it is depositedin the tiering chamber 34.

With regard to the magnitude and rate of translation of the hub 148about the shaft 46, it is pointed out that in any differential it isinherent that the spider gear will translate at one half the rotationalspeed of one side gear when the other side gear is held. In the presentcase, it is to be noted that the cam follower lever 154 provides motionamplification such that the cam track 151 translates the spider gear hub148 at half the velocity of the shaft 46 at 0 and at 180 in the cycle.Because the direction of movement of the hub is opposite at these pointsin the cycle, the output speed varies from 0 RPM to 120 RPM, or twicethe input speed of the shaft 46, and is readily provided for by means ofthe motion amplifying linkage and cam arrangement shown.

The shifter 26 (FIGS. 1 and 4) and the rocking differential 62 are bothdriven from the shaft 46 in timed

1. In a case loading apparatus including separator means for retainingone tier of containers for subsequent transfer into a case, and tieringfingers rotatable about a tiering shaft for transferring one tier percycle, said cycle initiating with said tiering fingers at a tier pickupposition adjacent said separator means and terminating at a tierdischarge position in a tiering chamber where groups of tiers areassembled into a case load; the improvement comprising a constant speedpower input shaft, a power transmission driven by said input shaft andhaving a cyclically variable output speed, and a power traininterconnecting said transmission and said tiering shaft, said tieringshaft rotating at inconstant speed during one tiering cycle, betweensaid tier pickup and said tier discharge positions, such that thetiering fingers accelerAte after picking up the tier of containers anddecelerate before discharging the containers to minimize shock damage tothe containers and the product therein.
 2. Apparatus according to claim1 wherein said transmission comprises a differential including an inputgear and an output gear on a common axis, a hub mounted for oscillatorytranslation about the axis of said gears, a spider gear carried by saidhub in meshed relation with said input and output gears, and power meansinterconnecting said hub and said power input shaft for oscillating saidhub, translation of the hub in one direction adding to the rotationalspeed of the output gear and translation in the other directionsubtracting from said rotational speed so that the input speed for saidpower train varies and said tiering shaft accelerates and decelerates.3. Apparatus according to claim 2 wherein said hub angularly oscillatessaid spider gear at a varying rate in one tiering cycle such thatsubtractive rotation of said output gear progressively decreases frominitiation of said tiering cycle to accelerate said output gear until itattains the speed of said input gear, said hub then reversing itsdirection of translation so that additive rotation of said output gearprogressively increases until said output gear attains twice the speedof said input gear at midpoint of the tiering cycle, said translatorymovements then repeating for the other half of the tiering cycle so thatsaid output gear decelerates in approaching the termination of saidtiering cycle.
 4. Apparatus for loading cases, the containers of thetype having a multi-lane feed conveyor with lane dividers that supplythe containers in a predetermined number of lanes to a tier former, thetier former having separator partitions aligned with said lane dividers;a drive including a rotatable shaft for raising tiering fingers upbetween said separator partitions for lifting a tier of cans out of theseparator; a shifter between said lane dividers and said separatorpartitions and having a plurality of shifter partitions of the samespacing as that of said separator partitions and said lane dividers; andmeans for laterally shifting said shifter back and forth over apredetermined stroke sufficient to cause said shifter partitions toblock the further passage of containers from the supply lane dividersinto the lanes between said separator partitions; the improvementwherein said tiering finger drive has means for initially slowly turningsaid shaft for gently raising the tiering fingers from a stationaryposition just below the bottoms of containers in said separator to aposition against the containers for allowing time for said shifter toblock the feed before the tiering fingers pick up the containers as wellas for causing the tiering fingers to pick up the containers gently,said tiering finger drive comprising means for thereafter acceleratingsaid shaft and hence the tiering fingers to complete the tier raisingoperation.